Stock feeding apparatus for punch presses and the like



Nov. 12, 1968 s. v. ROCH 3,410,151

STOCK FEEDING APPARATUS FOR PUNCH PRESSES AND THE LIKE Filed Oct. 11,1965 6 Sheets-Sheet l IN VEN TOR.

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STOCK FEEDING APPARATUS FOR PUNCH PRESSES AND THE LIKE Filed Oct. 11,1965 e Sheets-Shet 2 INVENTOR GERALD V. ROCH G. V. ROCH Nov. 12, 1968STOCK FEEDING APPARATUS FOR PUNCH PRESSES AND THE LIKE 6 Sheets-Sheet 5Filed Oct. 11, 1965 INVENTOR. GERALD V. RocH ZXLMMw/JM aw,

Alfornexs 5. v. ROCH 3,410,161

STOCK FEEDlNG APPARATUS FOR PUNCH PRESSES AND TEE LIKE Nov. 12, 1968 6Sheets-Sheet 4 Filed Oct. 11, 1965 gay f'Z/M INVENTOIR.

Affamc s AIR SUPPLY SOLENOID Nov. 12, 1968 G. v. ROCH STOCK FEEDINGAPPARATUS FOR PUNCH PRESSES AND THE LIKE Filed Oct. 11, 196

6 Sheets-Sheet 5 INVENTOA GERALD V. Rocu Nov. 12, 1968 G. v. ROCH3,410,161

TOCK FEEDING APPARATUS FOR PUNCH PRESSES AND THE LIKE Filed Oct. 11,1965 e Shets-Sheet e INVENYDR. GERALD V. ROCH Zf$-4WAJM M d-J UnitedStates Patent 3,410,161 STOCK FEEDING APPARATUS FOR PUNCH PRESSES ANDTHE LIKE Gerald V. Roch, New Augusta, Ind., assignor to E. L.

Humston Co., Inc., Indianapolis, Ind., a corporation of Indiana FiledOct. 11, 1965, Ser. No. 495,453

- 18 Claims. (Cl. 83-67) ABSTRACT OF THE DISCLOSURE Press apparatushaving stock feed means including pneumatically operated grippers andretainers, the gripper being on a slide linked to an eccentricmechanically driven by the press crank shaft, with mechanically drivenrotary valves mounted on the gripper and retainer directly for controlthereof. An override or retainer release mechanically driven and readilyadjustable by an external control knob for synchronization with diepilot pins. A misfeed detector including a carbide tipped verticallydisposed plunger tiltable upon detection of misfeed to operatecontactors in a press stopping circuit in the event of a press feederror. A scrap feed and chopper including a pneumatically actuatedgripper on a slide linked to an eccentric which is mechanically drivenby the press crankshaft, and a mechanically driven scrap retainerincluding a spring-biased cam-operated retainer shoe accommodatingvariations in stock thickness resulting from punch operation, and ascrap chopper including a shear blade following the scrap retainer andhaving a drive rod driven from the press crankshaft by an eccentric onthe crankshaft, the lower end of the drive rod being received in a ballbearing box, and a pair of tension rods mounted in suitable bearingsbetween the press crankshaft and the scrap feed and chopper bracket toprevent dislodging of the bracket by the scrap chopper action.

Background of the invention This invention relates generally to stockhandling equipment for metal working machines, and more particularly tometal stock feeding and scrap cutting apparatus employed in pressoperations.

In press operations, it is common practice to employ stock feedingapparatus at the input end of the press and at the scrap output end ofthe press for chopping the scrap strip into acceptable lengths anddepositing in scrap bins. Some equipment presently available isincapable of handling heavy strip stock, is highly sensitive tovariations in stock thickness and straightness, is incapable of reliablydetecting feed errors, responds too slowly to detection of feed errorsto avoid damage, applies exces sive loads to scrap cutter brackets, isinconvenient to adjust for proper relationship to the press operatingcycle or for feed length, or has other disadvantages. In addition togeneral inconvenience caused by such shortcomings, expensive machine anddie damage and down time can result.

It is therefore a general object of the present invention to improvestock feeding and scrap cutting functions in press operations.

A further object is to provide reliable and easily adjustable coil stockfeeding for presses.

A further object is to provide reliable and fast-acting detection of anyerrors in feeding, and machine shutdown in the event of error detection.

A further object is to provide high capacity scrap cutting apparatuswithout providing direct fioor support therefor.

A further object is to provide equipment achieving ice opposite ends ofthe press, the input feed apparatus serving to feed stock to the press,and the output feed apparatus serving to feed scrap from the press tothe scrap cutter for the cutting thereof and deposit in a scrapcontainer. The input feed includes a gripper mechanism and a retainermechanism, both of which are mounted on a bracket secured to the pressframe. Both of these mechanisms employ gripping members operable, whenactuated, to engage the metal stock adjacent thereto and force itagainst an anvil. Each of these gripping members is driven by an airoperated piston which is controlled by a rotary valve. The grippermechanism is mounted on a slide which is reciprocable on the brackettoward and away from the press frame by a positive mechanical drivewhich is so connected to the press crankshaft as to avoid any backlashor slippage. The same mechanical drive is used to control operation ofthe valves for the gripper mechanism and retainer mechanism.

Easily adjustable feed length adjustment and retainer release timingmeans are provided on the input feed apparatus. A selector lever is alsoprovided to release pressure -in both the feed gripper and retainersupplies, but an automatically operating cam is operable to override thefeed selector for replenishing the gripper and retainer air supplies intimely fashion when a new strip of stop is started through the machine,thus providing an automatic starting gage.

On the output feed, a gripper like that at the input feed is provided.The retainer at the output feed includes an active shoe member,mechanically driven by a cam which is mechanically driven by the outputfeed gripper drive, and a lower shoe serving as an anvil, with the stockbeing gripped between the shoes at the proper time. The cam and uppershoe are arranged to accommodate variations in thickness as well asburrs and bends in the scrap stock issuing from the press. The uppershoe also serves as a stripper for the scrap cutter which is positionedimmediately behind the output retainer.

The scrap cutter itself is driven directly from an cecentric on thepress crankshaft but tension rods are provided on the press crankshaftso that the load applied to the cutter from the cutter drive rod istaken largely in the tension rods, to minimize shear loads on the scrapfeed and cutter support bracket.

The full nature of the invention will be understood from theaccompanying drawings and the following description and claims:

FIG. 1 is a schematic elevational view in reduced scale, illustrating apress with stock supply and feeding apparatus and scarp feeding,chopping and disposal apparatus.

FIG. 2 is a fragmentary elevational view showing the vertical shaftdrive from the press and permitting height adjustment.

FIG. 3 is a perspective view of the stock input feeder.

FIG. 4 is a perspective view, partially in section, of the gripper slideand rotary valve mechanism therefor and drive therefor.

FIG. 5 is an enlarged fragmentary section through the 3 feed lengthadjustment and locking apparatus of FIG. 4.

FIG. 6 is an enlarged top plan view of the upper porting plate of therotary valve.

FIG. 7 is an enlarged top plan view of the rotary plate thereof.

FIG. 8 is an enlarged top plan view of the lower plate thereof.

FIG. 9 is a section taken at line 9-9 in FIG. 7 and viewed in thedirection of the arrows.

FIG. 10 is an enlarged perspective view, partially in section, of a feedlength detector, and showing schematically one example of circuitrywhich may be incorporated therewith.

FIG. 11 is a much enlarged fragmentary sectional view of the plungerlifting arm connection to the plunger.

FIG. 12 is a perspective view, partially in section, of the retainerportion of the press input feed apparatus, including the control valveand mechanical release therefor.

FIG. 13 is a fragmentary section therethrough illustrating the retainerrelease T bar and cam followers therefor.

FIG. 14 is a perspective view of the press output feed and scrap chopperapparatus.

FIG. 15 is a fragmentary side elevational view of the scrap stockgripper and retainer and drive therefor.

FIG. 16 is an enlarged fragmentary elevational view showing the chopperguide mounting.

Referring now to the drawings in detail, the press 11 includes a frame12, a ram 13 which is vertically reciprocable in the frame by rotationof the crankshaft 14 which is driven by the motor 16. In the illustratedembodiment, the crankshaft is driven by the motor through a combinationclutch and brake unit 15, the clutch portion of which is pneumaticallyengaged by air pressure applied through a solenoid valve 15a and, upondisengagement thereof, the brake is automatically applied to stop thepress crankshaft. Such units are well known in the art. A press feedbracket 17 is mounted to the frame at one end thereof and is verticallyadjustable thereon. An output feed and scrap cutter support bracket 18is mounted to the press frame at the opposite end thereof and is alsovertically adjustable.

Metal stock in the form of a strip 19 is supplied from a coil or roll 21and is fed through the press in the direction of the arrow 22. As thepress operates, the parts produced thereby may be discharged from one orthe other side thereof through the bottom and the punched out strip ofstock, which is now scrap, is cut in to desired lengths and deposited inthe scrap bin 23.

To drive the feed apparatus according to the present invention, positivedrive means are employed. Accordingly there is no slip between thecrankshaft and the stock gripper of the present invention, as willpresently become apparent. To achieve this result in the illustratedembodiment, a chain drive 24 is provided from the crankshaft to a rightangle drive box 26 mounted to the press frame 12. The right angle drivebox has a vertical output shaft 27 having a drive sprocket 28 splinedthereto, the sprocket 28 being mounted to the press feed support bracket17. Accordingly, when vertical adjustment of the press support bracketis required to obtain different feed line heights, as made possible bythe vertical slots 29 and bolts 31 connected to the press frame, thesprocket 28 can move up and down as required with respect to the driveshaft 27.

The sprocket 28 is connected by the roller chain32 to the sprocket 33secured to the lower end of a main press feed drive assembly 34.Sprocket 33 has arcuate slots therein receiving circularly spaced boltssecured in the bottom of the main press feed drive drum 36 which ismounted for rotation in the press feed support bracket, this rotationbeing on a stationary vertical axis therein. Accordingly, rotation ofthe press crankshaft causes rotation of the main press feed drive drum36, and one turn of the crankshaft causes one turn of the drum 36.

The press feed support bracket includes a pair of lower stock guides 37and a pair of upper stock guides 38, the upper stock guides beingdisposed immediately above the lower stock guides. The stock entersthese guides over the slack loop support rolls 39, between the edgeguides 41 and under the antibackup rolls 42. The antibackup rolls aremounted to a shaft 43 whose outer ends are connected to arms 44 whichare pinned at 46 to the press feed support bracket 17. Springs 47 holdthe antibackup rolls down on the stock to prevent the slack loop frompulling the stock away from the press at any time.

According to the present invention, retainer assembly 48 is provided onthe feed support bracket 17 and includes a feed stock retainer anvil 49afiixed to the bridge 51 but vertically adjustable by the use of theknob 52. While this anvil 49 is passive, being stationary, an activeretainer anvil 53 is provided directly below it and below the level ofthe top surface of the lower stock guides 37.

In order to move the stock from the slack loop to the retainer, thegripper assembly 54 is provided. This includes a gripper slide 56 whichis received in and supported by the gibs 57 having inwardly facing ways58 which happen to be V-shaped in the illustrated example. The slide ismovable in these ways toward the press in the direction of the arrow 59and away from the press in the direction of the arrow 61. Movement fromthe home position toward the press is accomplished during a feed strokeand the return stroke is in the direction of the arrow 61.

A bridge 62 is affixed to the press feed gripper slide 56 and has ananvil 63 afiixed thereto above the stock fed into the press butadjustable vertically by means of the knob 64. Immediately below thisanvil 63 is an active gripper anvil or gripper member 66, which isdisposed at nominally the same elevation as the retainer member 53,below the level of the upper surface of the lower stock guides 37.

The gripper member is actuated by an air piston which forces it upwardlyto grip the stock between the gripper member and the gripper anvil abovethe stock. The retainer member is operated in essentially the same way,but has a mechanical override feature also. Referring first, therefore,to the gripper member actuating means, a downwardly opening air cylinder67 has a flange supported in and bolted to the recess 68 in the gripperslide 56. This cylinder is symmetrical with respect to a vertical axis69 which, for convenience, can be considered centered horizontallybetween the ways or gibs 57. A piston 71 is received in this cylinderand sealed to the wall thereof by a sliding seal ring 72 and has anupwardly extending shaft to which the gripper member 66 is secured by ascrew 74. The piston is biased downwardly normally by the return spring76 and has a retainer plate 73 secured to the lower end thereof andrests against a stop which may be provided, for one example, in the formof an apertured plate member 88 of a rotary valve which will now bedescribed.

According to another feature of the invention, air pressure is appliedto this piston by means of a rotary valve assembly 78. This valveassembly is supported by a surge chamber member 79 having a flange 81thereon by which it is bolted to the underside of the gripper slide 56.Air is supplied from a source 82 which may be located anywhere, throughthe flexible pipe 83 and up through the hollow center passageway 84 ofthe shaft 77 and out through horizontal ports 86 to the surge tank. Acomparatively large quantity of air is thereby provided under pressurein the surge chamber 87.

The rotary valve includes upper and lower stationary porting plates 88and 89, respectively, the lower plate being sealed to the upper surfaceof the surge tank by an O-ring seal 91, and the upper surface of theupper valve plate being sealed to the air cylinder by the O-ring seal92. A rotary plate 93 is disposed between these plates and a sealing fitis provided between the upper surface of the rotary plate and the lowersurface of the upper plate, and between the lower surface of the rotaryplate and the upper surface of the lower plate. Appropriate spacing forachieving this sealing relationship and yet allowing freedom of rotationof the valve is provided by the spacer ring 94 between the plates andsurrounding the rotary plate.

As shown in the top plan views of these plates, the upper :plate 88 hastwo apertures 96 and 97 therein, spaced approximately 180 degrees apart.The rotary plate 93 has an arcuate aperture 98 therein which extendsapproximately 180 degrees, suitable support for the outer portion of theplate adjacent this port being provided by the spokes 99 which are notas thick as the plate and there-fore do not impede passage of airtherearound from one portion to the next adjacent portion of the port98. The lower plate 89 has the ports 101 and 102 therein which arelocated approximately 180 degrees apart. There may be an O-ring seal ina groove 103 on the lower face of the lower :plate around the port 102,for sealing to the upper surface of the surge tank where an exhaust orvent pipe 104 opens into the top surface of the surge tank. This ventpipe 104 passes through the surge tank and is open at its outer end toatmosphere. The operation of the rotary valve will best be understood ifthe means for providing the drive therefor, are first described.

The rotary plate drive shaft 77 passes upwardly through the stationarybushing 106 and therefore, through the surge tank, and is received in acentral aperture 107 of the rotary seal plate 93, the fit between theupper end of this drive shaft and the seal plate being sufiicientlyloose to avoid any binding between the rotary and sta tionary sealplates. The drive shaft is connected to a sprocket 108 pinned theretoand which is driven by a roller chain 109 which is, in turn, driven by asprocket 111.

The main press feed drive drum 36 is mounted in the press feed supportbracket 17 for rotation on a stationary vertical axis 112. Again, forpurpose of convenience, this axis should be considered located mid-waybetween the gibs 57, so that it is coplanar with the axis 69 in a planeparallel to the ways 58. This drum 36 is used to provide an eccentricdrive by means of a drive block 113 received in a dove-tail channel 114extending horizontally diametrically through the center of the drum. Ahearing block 116 is fixed in the drum and receives and supports a feedlength adjustment screw shaft 117 having the screw 118 thereon which isthreadedly received in the eccentric drive block 113. This adjustmentscrew has an outwardly opening tool receiving socket 119 therein whichis at the outer surface 121 of the drum. and facilitates insertion of anallen Wrench or other suitable tool therein for rotating the screw. Byrotating this screw, the position of the drive block 113 radially withrespect to the axis 112 can be varied to the extent desired. To lock theblock in any desired position, a wedge 122 is provided thereunder havingits lower surface on the upwardly sloping surface 123 in the drum andhaving a wedge advancing screw 124 threadedly received therein. Thiswedge advancing or fixing screw has a shaft 126 extending through andlongitudinally located by the bearing block 116. It has a tool receivingsocket 127 in the outer end thereof opening at the surface 121 of thedrum to permit insertion of an allen wrench or other tool for securingthe wedge tightly under the drive block once the block has been locatedas desired.

The drive block has an upwardly extending spindle 128 therein to whichis keyed or splined the sprocket mounting disc 110. Sprocket 111 ismounted on disc 110 and may have circularly spaced arcuate slots thereinthrough which the shanks of screws 110S- extend, these screws beingthreadedly received in disc 110 and securing the sprocket 111 thereto.One end of a slide operating link 129 is also connected to the spindle128 but is neither splined nor keyed thereto, being freely pivotallyattached thereto. The

other end of this link is received on the stationary cylindrical bushing130 surrounding the downwardly projecting cylindrical boss 79b at thebottom of the surge chamber, but is neither splined nor keyed theretoand is, in effect, only pinned thereto. Accordingly, as the drum 36 isrotated, if the spindle 128 is not concentric with the axis 112, it canserve to reciprocate the slide 56. The amount of reciprocation, andtherefore the feed length, is determined by the radial distance betweenthe axis 128a of the spindle and the feed drive drum axis 112. A preciseadjustment of this can be accomplished by the feed length adjustmentscrew 117 which has a gear 131 thereon geared to four digit drumregister or counter assembly 133, numerals of which can be viewedthrough the window 134 in the drum surface 121.

A mentioned previously, the positive drive from the press crankshaft tothe main press feed drive drum 36 is such that there is one revolutionof the drum 36 per one revolution of the crankshaft. The result is thatfor each revolution of the press crankshaft, the press feed gripperslide 56 is moved from home position toward the press for a feed strokeand is then moved back to home position to complete a feed cycle. Duringthis one revolution, there is to be one revolution of the rotary valveplate. This is achieved according to the illustrated embodiment of thepresent invention by making the sprocket 108 on the rotary plate driveshaft 77 the same size as sprocket 111 on the drive spindle 128.Therefore, assuming that the drum 36 rotates in the direction of thearrow 136, which is counterclockwise, the rotary valve plate 93 rotatesin the same direction. When the link 129 has returned the slide to nearhome position, so that longitudinal motion has reduced to a minimum, theleading edge 137 of the port 98 uncovers the edge 139 of the port 101 inthe lower plate and the edge 141 of the aperture 96 in the upper plate.Air from the surge tank immediately passes through the ports 101, 98,and 96 in succession and fills the area immediately under the gripperpiston 71 and starts forcing the piston upwardly. The gripper member 66engages the stock and forces it against the gripper anvil 63 to tightlygrip the stock. The clamping force thus achieved on the stock by thegripper can be established at any desired value, but a dimensioning ofparts to achieve 6300 pounds force at pounds per square inch pressureunder the gripper piston is considered satisfactory for manyapplications. As the leading edge 137 of the rotary plate meets theleading edge 141 of the upper stationary plate, the trailing edge 142 ofport 98 has already passed the trailing edge 143 of the upper plate andthe trailing edge 144 of the lower plate, so that there is no chance ofventing either the air from the surge chamber or air from underneath thepiston.

At the end of the feed stroke, the leading edge 137 of the rotary platemeets the leading edge 146 of the vent port 97 of the upper plate andalso meets the leading edge 147 of the vent port in the lower plate, tobegin venting air from the area below the piston. It is vented throughthe pipe 104 to atmosphere, this pipe being isolated from the surge tankalthough it passes through the same for convenience. Immediately priorto the beginning of the venting function, the trailing edge 142 of theport 98 in the rotary plate has passed the trailing edge 148 of port 101in the lower stationary plate and the trailing edge 149 of the port 96in the upper stationary plate, so that there is no loss of air from thesurge chamber to the atmosphere when venting begins. Also thedissipation of pressure under the gripper piston is accomplished rapidlyfor a positive release of the gripper member from the stock.

In order to be sure that the timing of the sequence of valve eventscorresponds properly with the timing of the feed and return strokes, itis necessary that the stationary plates be secure from rotation and thiscan be accomplished by a dowel pin 151 into the surge tank or pistoncylinder. Also the fit between the aperture 107 and the drive key upperend of the rotary plate drive shaft 77 must be accurate enough to avoidrotational backlash and yet loose enough to avoid binding. Finally, tochange value timing with respect to the slide movement, the

'screws 1105 may be loosened to permit sprocket 111 to rotate withrespect to its drive spindle 128 to the extent permitted by the arcuateslots in the sprocket. The screws can then be tightened. Other meanscould also be employed, but facility for adjustment is desirable.

The press input feed retainer member 53 is actuated in much the samemanner as is the press input feed gripper member. There is included thecylinder 153 afiixed to the input feed support bracket and receiving theretainer actuator piston 154 therein, with the ring seal 156 beingprovided therebetween. The rotary valve construction is the sameincluding lower and upper stationary plates which may be similar tothose for the gripper control valve and a rotary valve plate which mayalso be similar. It may be desirable, however, to provide a lowerclamping force for the retainer, such as 1900 pounds at 100 pounds persquare inch in the surge chamber, for example. Accordingly, diameters ofthe piston seal and cylinder would be less than that for the gripperpiston. For conservation of space, therefore, the valve plates can besmaller than those provided for the gripper. As is the case with thegripper, the piston rod is received in and supported by an oilcontaining bushing 157 mounted in the air cylinder.

The rotary valve plate 158 for the retainer control valve is driven by asleeve 159 afiixed to or a part of a disk 161. The upper end of thesleeve may be rectangular or some other configuration fittingly receivedin a matching central aperture in the rotary plate 158, similar to thatfor the gripper control valve, to enable the sleeve to drive the plate.The drive for the disk 161 is provided by a sprocket 162 mounted to thedisk and affixed thereto by the nuts 163 received on upstanding studs164 in the disk 161, there being the arcuate slots 166 in the sprocketto accommodate rotational adjustment for timing the valve event sequencewith respect to the operation of the drum 36, and therefore with respectto the operation of the gripper feed slide. This timing is arranged sothat as the roller chain 167 driven by the drum 36 drives the rotaryvalve for the retainer, and the slide is moved by the crank link 129,pressure is applied under the piston in the retainer immediately beforerelease of pressure from the piston in the gripper so that for a shortinterval the stock is clamped by both the gripper and the retainer.Thereafter, the pressure remains under the piston in the retainer untilthe slide has again returned home and clamping pressure has again beenapplied to the gripper piston. Thereupon the retainer control valvereleases pressure from under the retainer piston allowing it to unclampdue to the action of the piston return spring therefor.

One important feature of the construction of the retainer according tothe present invention is the retainer override or release means employedto permit the proper functioning of the die pilot pins commonly used indie sets to precisely locate stock in the press during the actualforming operation. In the retainer assembly, the shaft 168 passing upthrough the center of the valve drive sleeve 159 serves as the retainerrelease shaft. The disk 169 at the upper end thereof is secured to theretainer piston 154 by bolts 170, for example, so that the release shaftand piston are operable in unison. In other Words, if the piston rises,so does the release shaft and if the release shaft is held downwardly,so is the piston held downwardly.

At the lower end of the retainer release shaft there is a horizontal bar171. This bar has two cam follower rollers 172 and 173 therein, follower172 being disposed at a different radius with respect to the axis 174than is the follower 173. Both of these followers are disposed below thedisk 161 on the valve drive sleeve lower end,

and the disk 161 has two retainer release cams 176 and 177 thereon. Cam176 is a downwardly projecting cam and is disposed at a radius from theaxis 174 such as to enable engagement with the follower roller 172. Thecam 177 is closer to the center of the disk 161 and degrees away fromthe cam 176 and is engageable with the follower roller 173.

The spacing of the upper surfaces of the cam follower rollers 172 and173 with respect to the lower face of the disk 161 is such that whenthere is no pressure applied under the retainer piston 154, there is nocontact between the disk 161 or the cams 176 and 177 thereon, and thefollower rollers. In contrast, however, when the air pressure is appliedunder the piston 154 to move it up so that it can grip stock between thegripper member and the gripper anvil, the follower rollers areengageable by the cams, roller 172 being engageable by cam 176 androller 173 being engageable by cam 177. Accordingly, as the disk 161 isrotated by the sprocket 162, and also rotates the control valve rotaryplate, the retainer release bar 171 is driven downwardly once perrevolution by the cams 176 and 177 to overcome the air pressure appliedto the retainer piston and drive it, and therefore the retainer member,downwardly to release the stock. This is done so that once the press diepilot pins have entered locating holes in the stock, they can preciselylocate the stock in the press and the retainer member interferes in noway with this precise locating function. The provisions of two cams andfollowers is to rather evenly distribute the load downwardly on theshaft so as to avoid undue cocking forces. The two followers and twocams are located on different radii to avoid releasing the retainertwice per revolution, rather than the one time desired per revolution.

The pilot release timing with respect to the press crankshaft is madeadjustable by mounting the T-bar 171 in a channel 178 in a gear wheel179 mounted in the feed support bracket 17 for rotation on the axis 174.The channel 178, which extends diametrically across the gear wheel inthe upper surface thereof fits the bar 171 so that upon rotation of thegear wheel 179, the bar is rotated also, without any backlash. Althoughthere is a close fit between the sides 181 of the bar and the sides ofthe channel 178, the bar can still move up and down in the channel topermit retainer release by the release cams. The gear wheel 179 isnormally clamped in a desired rotational position by the encirclingsplit clamp 182 which is split at 183 and has a tightening screw 184therein to aflix the gear wheel at any desired rotational position. Tofacilitate rotation of the gear wheel, a release timing adjustment knob186 is provided on the shaft 187 on which is mounted the worm 188engaging the gear 189 on the gear wheel. This knob 186 extends out fromthe front of the feed support bracket for easy access, and the gearwheel clamping screw may have a tool receiving socket 191 therein alsoexposed at the outside of the mounting bracket 17, adjacent the knob.Therefore, to adjust the timing of the release, with respect to thecrankshaft position, it is necessary only to release the clamp by meansof the screw therefor and adjust the knob 186 appropriately.

Further with reference to the retainer, a vent pipe 192 is providedwhich passes through the surge tank and discharges to atmosphere at thebottom of the surge tank. However the air supply does not come throughthe central shaft as it does in the gripper, but rather is provided bythe conduit 193 entering the wall of the surge tank. This conduit isalso connected to the air supply source 82. However the connection fromthe air supply source 82 to the conduit 193 for the retainer and theconduit 83 for the gripper, is provided by means of a manual valve 194.This valve, which may be a conventional valve, has at least twopositions. In one of these positions it connected the conduits 83 and193 to the supply source 82 and in the other position closes olf thesupply source 82 and vents the conduits 193 and 83 to atmosphere as atthe vent port 196. A sequence selector lever 197 having a knob 198 atthe outer end thereof and outside the feed support bracket, is shownschematically connected to the manual valve. When this selector lever isin the up position it applies pressure from the source to the twoconduits 83 and 193. When it is in the down position it vents the supplyconduits and shuts off the connection to the source. An automaticstarting gage is provided in connection with this sequence selector. Theautomatic starting gage includes a cam 199 which, for convenience, isshown mounted to the sprocket 33 and is engageable with a linkagedesignated by the dotted line 201 which when actuated by the cam servesto move the selector lever 197 from the release position to the runposition.

In the use of the sequence selector, once the supply of stock from thesupply roll 21 has been exhausted at the feed side of the machine, thesequence selector can be pushed downwardly to the release position onthat which ever of the gripper or retainer pistons is pressurized willbe depressurized, so that neither the gripper nor retainer is tending togrip stock. This sequence selector is left in the release position, butthe cam 199 is located so that after the gripper slide has moved towardthe press to its inmost point and the control valve for the grippermember has moved to a point where it closes off the supply to thegripper piston, the cam 199 moves the sequence selector to the upper orrun position so that the manual valve 196 no longer vents the air supplyconduits and air is again supplied from the source 82 to the gripper andretainer surge chambers. Accordingly the gripper is enabled to grip anew strip of stock for the next feed stroke.

To avoid damage which could possibly occur if the stock slipped in thegripper during a feed stroke, a feed length or 'rnisfeed detector isemployed according to another feature of the present invention. Thisincludes a housing afiixed to the bridge 62 on the press feed gripperslide. A plunger guide cylinder 203 is pivotally mounted on a horizontalaxis 204 by means of the trunnion pivot pins 206 received in oppositefaces of the housing 202. Accordingly, the guide cylinder 203 can pivottoward and away from the bridge, the axis 204 being perpendicular to thedirection of travel of the gripper slide. The cylinder has a cylindricalaxis 207 which is normally maintained in a vertical position by thesnubber or centering springs 208 and 209 disposed between opposite endwalls of the housing and the wall of the guide cylinder at diametricallyopposed points.

A reference plunger 211 is guidingly received in the guide cylinder 203and has a carbide tipped pointed lower end 212. The plunger has theannular flange 213 therein against which the plunger actuating spring214 is seated at its lower end, the upper end of the spring being seatedon the inwardly turned flange 216 at the upper end of the guidecylinder. Accordingly the plunger is normally biased downwardly and thespring and plunger tip are usually selected so that a very slightpenetration of the stock being used can be obtained if the plunger isallowed to rest against the stock with the force applied to the plungerby the spring 214.

From the foregoing description, it should be understood that if theplunger is allowed to rest on the stock being gripped by the grippermember, there will be no tipping of the plunger during the feed strokeand the axis 207 will remain vertical, unless there is some longitudinalslippage or movement of the stock with respect to the gripper. If thestock slips in the gripper, so that less than the proper amount of stockis fed into the press during the feed stroke, the lower point of theplunger resting in the dent it made in the stock will move away from thegripper bridge, slightly tipping the upper end toward the bridge. Thistipping effect is utilized immediately to stop the press. This isaccomplished by providing a pair of fixed electrical contactors 217 and218 mounted to the detector housing 202 and insulated therefrom. Anelectrically conductive strip 219 may be placed around the cylinder 203and secured thereto but electrically insulated therefrom and providedwith contactors 221 and 222 at opposite ends thereof. It will beapparent, therefore, that if the plunger guide cylinder tips in responseto tipping of the plunger, these contactors 221 and 222 will move towardor away from the gripper slide bridge. In so doing, contact of one ofthese contactors will be broken with the fixed, housing-mountedcontactor which is normally electrically contacting it. Accordingly thepress stop circuit 223 is broken. This stop circuit can be any one of avariety of constructions but for purposes of illustration it may beconsidered the holding coil circuit for a relay armature 224, the stopcircuit including the holding coil 226, the contactors 227 and thetransformer 228. If the relay armature is moved in the direction of thearrow 229, either manually or by solenoid action, the coil 226 iseffective to hold the armature in position keeping the contact points227 closed to complete the stop circuit. At the same time, the switch231 from the electrical supply 230 to the solenoid 15b for clutch supplyvalve 15a is closed. Two lines from the electrical supply 23.0 are usedto supply the primary winding of transformer 228. Accordingly, if theplunger tips, it will break the stop circuit and allow the spring loadedmain line relay armature 224 to move in the direction of the arrow 232and open the line switch 231 and the crankshaft drive clutch (FIG. 1)will be disengaged and the crankshaft brake applied to stop the press.

In order to raise the plunger at the proper time and permit descentthereof at the proper time, a detector control cam 233 is provided whichis secured to or part of the sprocket 10-8 and therefore driven by thegripper slide valve drive chain 109. This cam is followed by a detectorcontrol cam follower assembly including a roller 234 1nounted on thelever 236- pivoted to the gripper slide at 237. The other end of thislever engages the crank arm 238 connected to the shaft 239 received inthe bushing sleeve 241 affixed to the gripper slide bridge. At the otherend of the shaft 239 the crank 242 is secured and is provided with ayoke 243 at its distal end and receiving the upper end of the plungertherein. A knife edge bar 244 extends across the yoke through anaperture 246 in the upper end of the plunger. This bar has a knife edge247 at the upper margin thereof which is directly aligned with thevertex 248 of the downwardly opening notch of the aperture in theplunger. The length of the plunger aperture measured in a directionperpendicular to the plunger axis and tangent a circle concentric withthe plunger guide pivot axis 204 is great enough to permit the plungerto tip either toward or away from the slider bridge, which is thereforea tipping in the direction of the feedstroke or directly opposite thefeed stroke, without interference from the knife edge bar. At least nointerference occurs until the tipping is sufiicient to break the pressstop circuit. This relationship can be achieved readily.

The detector control cam is located to lift the plunger at the end ofthe feed stroke, and then permit its descent to penetrate the stockagain immediately before the next subsequent feed stroke. Accordinglythe timing of this particular cam can be essentially the same as thetiming for the application and venting of pressure at the gripperpiston. The plunger guide and plunger assembly is arranged so that atall times the center of gravity thereof is located very near the pivotalaxis 204 so that tipping which might otherwise result from inertiaeffect is avoided, and there will be no false stops of the machineeither during the feed stroke or return stroke of the gripper slide.

The press scrap output and chopper feed apparatus is very much like thepress input feed apparatus, so far as the gripper and drive therefor areconcerned. However the scrap feed gripper assembly employs an upper shoe251 instead of a circular button type anvil employed in the press feedgripper, and also a lower shoe 252 instead of the small circular buttontype of gripper member. These shoes extend across the scrap stockissuing from the press and are able to properly grip the scrap eventhough there may be very little available area for gripping because ofthe absence of material which has been punched out of the stock by thepress. Just as with the press feed gripper slide, the chopper feedgripper slide is driven by a chopper feed drive drum assembly 253 andcrank link 254, the drum assembly being driven by positive drive meansincluding a drive chain and right angle drive means or shafting in thehousing 257 from a sprocket on the crankshaft 14. A feed lengthindicating register 258 like register 134 is provided in the drumassembly 253 and is visible through the opening 259 in the front face ofthe scrap feed and chopper support bracket 18. The scrap feed lengthadjusting screw 261 and eccentric block clamping screw 262 are alsovisible and accessible through the opening for adjustment, just as inthe case of the press feed drive drum assembly.

The scrap chopper includes some components of conventional constructionand others which are new in and of themselves or are disposed in a newarrangement. A lower shear blade 262 is secured in position by the lowerblade holder plate 263 and is disposed adjacent the bow tie type ofupper shear blade 264 mounted in the upper blade holder or ram 266.Whereas conventional upper blade holders are guidingly received on apair of guide pins 266a which are only secured to the output bracket attheir bottoms, it is a feature of the present invention to also afiixthese guide pins to the bracket at the tops as shown at the bosses 267mounted on the bracket 18. Bending of these guide pins is therebyavoided and the force which can be used for shearing heavy stock isincreased substantially. Each of the upper blade holder guide pinsfittingly receives guide bushings 268 affixed in the upper blade holder.Accordingly the holder is vertically reciprocable with precision forcutting the scrap Where the upper and lower shear blades meet during thedownstroke.

To operate the blade holder, a driving member 269 is employed which ispinned at 271 to the blade holder and at one end by a shear pin 272 tothe links 273 which are mounted on the shaft 274 mounted on the outputbracket. A conventional ball-box and sea assembly is provided at 276which is at the opposite end of the blade driving member and receivesthe lower end ball 277 of the blade drive rod 278, the upper end of thedrive rod being connected to a collar 279 eccentrically mounted on thecrankshaft whereby the drive rod is moved up and down once for eachrevolution of the crankshaft of the press.

According to one feature of the invention, the pin 272 is a shear pin sothat if the resistance of the scrap to cutting is excessive, which couldresult from a dull blade, for example, no damage will be done other thanthe shearing of this particular pin. However it is desirable to be ableto cut very heavy stock for long periods of time. It is also desirableto be able to vertically adjust the output support bracket 18 toaccommodate different feed line heights. For this purpose the mountingis much like that illustrated for the input bracket. Such mountings havein the past, however, severely limited the capacity of the chopper andinstances have occurred where the scrap cutter bracket has actually beenpushed downwardly on the machine out of position to properly receive thescrap stock therefrom, a situation which can result in substan tialdamage. Accordingly it is another feature of the present invention toavoid this result, and this is accomplished by employing a pair oftension rods 281 and 282 which are pinned at their upper end to a hanger283 having a hearing therein by which it is precisely received on thecrankshaft 14 and supported thereby. The lower ends of these rods areprovided with yokes 284 pinned to the side plates 236 of the bracket 18by pins 287. The yoke portions have upwardly extending threaded studportions 288 threadedly received in the connectors 289 which arethreadedly received on the lower ends of the upper rod portions, withthe lock nuts 291 and 292 being also provided. In this manner the lengthof each of the tension rods can be precisely adjusted to accommodate thefee-d line height desired and yet actually serve to support the outputbracket, the pins 287 having their axes substantially coplanar in avertical plane with the center point of contact between the lower ball277 of the drive rod and the ball bearing box assembly 276. Thereforethe downward force exerted by the drive rod is not taken by the bracketmounting bolts or studs 293, but rather by the tension rods 281 and 282according to one of the features of the present invention. A jack screw294 threadedly received in a boss 296 affixed to the press frame andhaving an upper end in a conventional adjusting screw stud cap mountedto the output feed bracket 18 may be employed to facilitate raising andlowering the bracket to obtain various feed line heights. Of course thetension rod lengths and drive r-od lengths must be changed at the sametime.

The scrap retainer differs from the feed stock retainer and includes anupper shoe 297 above the top surface of the stock 298, the lower surfaceof which runs on the support member 299 which is part of the bracket andto which the lower shear blade 262 is mounted. This upper shoe has afollower member 301 on the upper surface thereof engaged by the retainerdrive cam 302 mounted on shaft 303 driven by a sprocket 304. Sprocket304 is driven by a drive chain 306 which is in turn driven by thesprocket 30 7 connected to the output shaft of a right angle drive box308 whose input shaft 309 is driven by sprocket 311 driven by a chain312 from sprocket 313 connected to the output and scrap chopper feeddrive assembly. This cam 302 is operable to drive the retainer shoe 397into engagement with the scrap stock 296 issuing from the press and holdit clamped against the member 299 during the desired retainer periodonce for each revolution of the press crankshaft. Although the cam shaft303 is supported in bearings 314 at its opposite ends which are, inturn, supported in the side plates 286 on the output support bracket 18,it is desirable to accommodate some very limited vertical action of thecam shaft 303. For this purpose high load coil springs 316 are providedbetween the cam shaft bearing blocks and the upper abutments 317connected to the side plates. This allows some limited vertical actionof the cam shaft 303 which results in precision retainer action and yetaccommodates some variation in the scrap stock which will naturallyresult from burring and bending which occurs during the press work onthe stock.

Timing of this retainer to the press operation may be readilyaccomplished by providing arcuate slots in any one of the many drivesprockets therefor, or by other suitable means.

A sequence selector knob 318 is provided for the output feed just as itis for the input feed, but it only effects the output gripper in thesame way as does the input sequence selector affect the input gripper.It has no effect on the output and scrap chopper feed retainer.

Because of the location of the shoe 297 of the output retainer, it alsoserves as a stripper for the upper shear blade, being locatedimmediately adjacent thereto and immediately above the scrap stockissuing from the machine. It will be observed that a portion of thisretainer shoe actually extends above the top surface of the lower shearblade 262. The retainer shoe has the coil springs 321 which are returnsprings and normally biased upwardly. The upper shoe 297 of the cutterfeed retainer is spring biased upwardly by the springs 321 and the inneredge thereof is curved upwardly at 322 and the receiving edge of thebracket member 299 is curved downwardly at 323 to facilitate receipt ofthe stock therein and passage therethrough, By having the portion 32-4of the shoe 297 disposed immediately adjacent the upper shear blade, it

not only serves as a stripper for the blade, but prevents the scrapfront edges from abutting against the upper shear blade as the scrap ismoved through the chopper after each down stroke of the upper shearblade.

It was mentioned previously, that the input gripper may be convenientlyset to apply force of 6300 pounds at 100 pounds per square inch airpressure. This pressure may also be used for the output gripper and thesame load may also be used. However it is more likely that a load in theneighborhood of 1900 pounds would be employed in most cases at theoutput gripper. A typical air consumption for 300 press strokes perminute and 100 pounds per square inch is 3 cubic feet per minute. Theseloads, pressures, and speeds, and volumes, are given merely as examples.Many others will be found useful in practice.

From the foregoing description, it is believed that the presentinvention can be understood and then it will be seen that the presentinvention is well able to achieve the objects set forth herein.

While the invention has been disclosed and described in some detail inthe drawings and foregoing description, they are to be considered asillustrative and not restrictive in character, as other modificationsmay readily suggest themselves to persons skilled in this art and withinthe broad scope of the invention, reference being had to the appendedclaims.

The invention claimed is:

1. In press apparatus the combination comprising: .(A) a press framehaving therein,

(1) apressram,

(2) a powered crankshaft connected to said ram for driving said ram inreciprocating manner, one complete rotation of the crankshaft providinga press cycle,

(B) press feed apparatus including,

(1) a press feed support bracket mounted to said press frame,

(2) a main press feed drive member rotatable on a stationary firstvertical axis in said bracket,

(3) positive drive means connected between said main drive member andsaid crankshaft for driving said main drive member in synchronism withsaid crankshaft without slippage therebetween,

(4) a reciprocable gripper slide movable on said bracket toward and awayfrom the press frame,

(5) retainer apparatus on said bracket between said slide and said pressframe,

(6) a slide drive link pivotally attached to said slide andeccentrically mounted to said main drive member and operable during onerevolution of said drive member to reciprocate said slide from a homeposition toward said press frame and back to home position to provideone press feed cycle,

(7) a press feed gripper mounted to said slide and including an anvilabove the stock and a gripper member below the stock with the grippermember having a fluid operated gripper clamping piston connected theretoand a rotary control valve therefor,

(8) second positive drive means connected to said main drive member andto said gripper control valve and operable during a feed cycle to drivesaid gripper control valve through one complete sequence of valve eventsto move the gripper member toward the gripper anvil and clamp the stocktherebetween and then move said stock toward said press frame as saidmain drive member moves said slide toward said press frame, thusperforming a press feed stroke, and then permit said gripper member tomove away from said gripper anvil and release said stock prior to returnof said slide to its home position to complete a press feed cycle.

2. In press apparatus, the combination comprising: (A) a press ram,

(1) apressram,

(2) a powered crankshaft connected to said rarn for driving said ram inreciprocating manner, one complete rotation of the crankshaft providinga press cycle,

(B) press feed apparatus including,

(1) a press feed support bracket mounted to said press frame,

(2) a main press feed drive member,

(3) positive drive means connected between said main drive member andsaid crankshaft for driving said main drive member in synchronism withsaid crankshaft without slippage therebe tween,

(4) a reciprocable gripper slide movable on said bracket toward and awayfrom the press frame,

(5) slide drive means attached to said slide and to said main drivemember and operable during one revolution of said drive member toreciprocate said slide from a home position toward said press frame andback to home position to provide one press feed cycle,

(6) a press feed gripper mounted to said slide and including an anviland a gripper member with the stock disposed therebetween, the grippermember having a fluid operated gripper clamping piston and a controlvalve for said piston, and

(7) a press feed stock retainer having an anvil aflixed to said bracketabove the stock and a retainer member below said retainer anvil, saidretainer member having a retainer clamping piston thereunder with aretainer rotary control valve and surge chamber under said retainerclamping piston,

(8) second positive drive means connected to said main drive member andto said gripper control valve and operable during a feed cycle to drivesaid gripper control valve through one complete sequence of valve eventsto move the gripper member toward the gripper anvil and clamp the stocktherebetween and then move said stock toward said press frame as saidmain drive member moves said slide toward said press frame, thusperforming a press feed stroke, and then permit said gripper member tomove away from said gripper anvil and release said stock prior to returnof said slide to its home position to complete a press feed cycle.

3. In press apparatus, the combination comprising: (A) a press framehaving therein,

(1) a press ram,

(2) a powered crankshaft connected to said ram for driving said ram inreciprocating manner, one complete rotation of the crankshaft providinga press cycle,

(B) press feed apparatus including,

(1) a press feed support bracket mounted to said press frame, (2) a mainpress feed drive member,

(3) positive drive means connected between said to drive said retainercontrol valve through one complete sequence of valve events to causesaid retainer clamping piston to move said retainer member to clamp thestock at the beginning of a pause in the feeding thereof and tend tokeep said stock clamped by said retainer member during the pause, and

(6) retainer release means including a retainer release cam driven bysaid another positive drive means, and a cam follower connected to saidretainer member and operable by said release cam in opposition to theforce applicable to said retainer member by said retainer piston to movesaid retainer member away from said retainer anvil and release the stockto accommodate precise positioning of stock in the press by die pilotstherein, said retainer release cam being operable once during each presscycle to thereby permit die pilots to precisely position the stock inthe press frame immediately prior to stock forming action by said pressram, and said retainer release means including adjustable release timingmeans incorporating a follower receiver positioning the release camfollower and externally adjustable whereby the index of the release camfollower with respect to the press crankshaft is easily adjustable toproperly time the release of said retainer member with the action of thepi lots.

4. In press apparatus, the combination comprising: (A) a press framehaving therein,

(1) a press ram,

(2) a powered crankshaft connected to said ram for driving said ram inreciprocating manner, one complete rotation of the crankshaft providinga press cycle,

(B) press feed apparatus including,

(1) a press feed support bracket mounted to said press frame,

(2) a main press feed drive member,

(3) positive drive means connected between said main drive member andsaid crankshaft for driving said main drive member in synchronism withsaid crankshaft without slippage therebetween,

(4) a press feed stock retainer having an anvil and a retainer rnemberwith the feed stock disposed therebetween, said retainer member having aretainer clamping piston connected thereto and a retainer control valvetherefor,

(5) another positive drive means connected to said main drive member andto said retainer control valve and operable during a press cycle todrive said retainer control valve through one complete sequence of valveevents to cause said retainer clamping piston to move said retainermember to clamp the stock at the beginning of a pause in the feedingthereof and tend to keep said stock clamped by said retainer memberduring the pause, and

(6) retainer release means including a retainer release cam driven bysaid another positive drive means, and a cam follower connected to saidretainer member and operable by said release cam in opposition to theforce applicable to said retainer member by said retainer piston to movesaid retainer member away from said retainer anvil and release the stockto accommodate precise positioning of stock in the press by die pilotstherein, said retainer release cam being operable once during each presscycle to thereby permit die pilots to precisely position the stock inthe press frame immediately prior to stock forming action by said pressram, and said retainer release means being adjustable to prop- 16 erlytime the release of said retainer member with the action of the pilots.

5. Press feed apparatus comprising:

(1) a press feed support bracket mountable to a press frame;

(2) 'a press feed drive member rotatable on an axis in said bracket;

(3) means on said press feed drive member adapted to operation by apress crankshaft for driving said press feed drive member in synchronismwith the crankshaft;

(4) a reciprocable gripper slide movable on said bracket;

(5) retainer apparatus on said bracket;

(6) a slide drive link pivotally attached to said slide and to aneccentrically mounted radially adjustable block in said press feed drivemember and operable during one revolution of said drive member toreciprocate said slide from a home position a selectable distance for afeed stroke and then back to home position to provide a press feedcycle;

(7) a press feed gripper mounted to said silde and including an anviland a gripper member spaced apart to accommodate receipt of press feedstock therebetween, with the gripper member having a fluid operatedgripper clamping piston connected thereto and a rotary control valveconnected to said piston and to a pressurized fluid containing chamberto control operation of said gripper clamping piston;

(8) a drive sprocket affixed to said press feed drive member and adriven sprocket connected to said gripper control valve, with a chainconnecting said sprockets for power transmission therebetween, bothsprockets being of the same size whereby said press feed drive member isoperable during a feed cycle drive said gripper control valve throughone complete sequence of valve events to move the gripper member towardthe gripper anvil and clamp the stock therebetween and then move awayfrom said home position, thus performing a press feed stroke, and thenpermits said gripper member to move away from said gripper anvil andrelease the stock prior to return of the slide to its home posion tocomplete a press feed cycle;

(9) said retainer apparatus including a retainer anvil and a retainermember spaced apart to accommodate press feed stock therebetween, withthe retainer member having a fluid operated retainer clamping pistonconnected thereto and a retainer control valve connected to saidretainer clamping piston and to a pressurized fluid chamber, and a thirdsprocket connected to said press feed drive member and a fourth sprocketconnected to said retainer control valve with a second chain connectingsaid third and fourth sprockets, said third and fourth sprockets beingof the same size whereby said main drive member is operable during afeed cycle to drive said retainer control valve through one completesequence of valve events to move said retainer member to clamp the stockwhen movement of the slide away from said home position has terminatedand tend to keep said stock clamped by said retainer member until saidslide starts away again from home position;

(10) retainer release means mounted in said press feed support bracketand including a retainer release cam driven by said second chain and acam follower connected to said retainer member and operable by saidretainer release cam in opposition to the force applicable to saidretainer member by said retainer piston, to move said retainer memberaway from said retainer anvil and release the stock, to thereby permitprecise positioning of stock in a press by die pilots in the press.

6. Machine feed appartus comprising:

(1) a machine feed support bracket mountable to a machine frame;

(2) a machine feed drive member rotatable in said bracket;

(3) means on said machine feed drive member adapted to operation by amachine crankshaft for driving said drive member in synchronism with themachine crankshaft;

(4) a reciproca'ble gripper slide movable on said bracket;

(5) a slide drive link pivotally attached to said slide and to aneccentrically located point on said drive member and operable during onerevolution of said drive member to reciprocate said slide from a homeposition to a point for a feed stroke and then back to home position, toprovide a machine feed cycle;

(6) a machine feed gripper mounted to said slide and including anvilmeans and gripper means spaced apart to accommodate receipt of machinefeed stock therebetween, with the gripper means having a fluid operatedgripper clamping piston connected thereto and a rotary control valveconnected to said piston and to a pressurized fluid source to controloperation of said gripper clamping piston;

(7) a first drive sprocket affixed to said drive member and a drivensprocket connected to said gripper control valve, with a chainconnecting said sprockets for power transmission therebetween, bothsprockets being of the same size whereby said main drive member isoperable during a feed cycle to drive said gripper control valve throughone complete sequence of valve events to move said gripper means towardsaid gripper anvil means and clamp the stock therebetween and then moveaway from said home position, thus performing a machine feed stroke, andthen permits said gripper means to move away from gripper anvil meansand release the stock prior to return of the, slide to its home positionto complete a machine feed cycle.

7. Machine feed apparatus comprising:

(1) a machine feed support bracket mountable to a machine frame;

(2) a machine feed drive member rotable in said bracket;

(3) means on said machine feed drive member adapted to operation by amachine drive means for driving said drive member in synchronism withthe machine drive means;

(4) a reciprocable gripper slide movable on said bracket;

(5) a slide drive shaft eccentrically mounted to said drive member andconnected to said slide and operable during one revolution of said drivemember to reciprocate said slide from a home position to a point andthen back to home position to provide a machine feed cycle;

(6) a machine feed gripper mounted to said slide and including anvilmeans and gripper means spaced apart to accommodate receipt of machinefeed stock therebetween, with the gripper means having a fluid operatedgripper clamping piston connected thereto and a control valve connectedto said piston and to a pressurized fluid source to control operation ofsaid gripper clamping position;

(7) and valve drive means connected to said drive member and driventhereby whereby said drive member is operable during a feed cycle todrive said gripper control valve through a sequence of valve events tomove said gripper means toward said gripper anvil means and clamp thestock therebetween and then move away from said home position, thusperforming a machine feed stroke, and then permits said gripper means tomove away from said gripper anvil means and release the stock prior to18 return of the slide to its home position to complete a machine feedcycle.

8. A device set forth in claim 7 and further comprising:

(1) a stock engaging detector member biased toward engagement with stockgripped in said gripper, said detector member being mounted to saidslide for movement with respect thereto upon relative movement betweensaid stock and said slide when said stock is engaged by said engagingmember;

(2) machine control means including a portion operatively associatedwith said st-ock engaging member and operable upon relative movementbetween said engaging member and said slide caused by relative movementbetween said slide and the stock when the engaging member engages thestock, to enable termination of machine operation;

(3) and release means driven by said drive member and connected to saidengaging member to release said engaging member when the stock isreleased by said gripper means to accommodate return of said slide tohome position without activation of said machine control means.

9. In a machine feeding apparatus, a retainer comprising:

(l) a retainer anvil and a retainer member spaced apart to accommodatemachine feed stock therebetween;

(2) a fluid operated retainer clamping piston connected to said retainermember;

(3) a rotary retainer control valve, and a pressurized fluid chamberunder said control valve, said valve and said chamber being disposedunder said clamping piston, and said valve being operable to connectsaid chamber to said piston at certain times to permit passage ofpressurized fluid from said chamber to said piston for operating saidpiston and thereby operating said gripper member to clamp stock againstsaid anvil;

(4) a drive member connectable to machine drive means for operation insynchronism therewith;

(5) a first sprocket connected to said drive member and a secondsprocket connected to said rotary valve and a drive chain connectingsaid sprockets and driving said valve to control the admission ofpressurized fluid to said piston and the venting of pressurized fluidfrom said piston to atmosphere, to cause said retainer clamping pistonto first move said retainer member to clamp stock at the beginning of apause in the feeding of the stock and tend to keep the stock clamped bysaid retainer member during the pause, and then relieve pressure fromsaid clamping piston to allow the retainer member to unclarnp the stock;

(6) retainer release means including a retainer release cam driven bysaid second sprocket, an inverted T-bar having the central shaft thereofextending centrally up through said chamber and said valve and connectedto said retainer member, said T-bar having cam follower rollers the-reinoperable by said release cam in opposition to the force applicable tosaid retainer member by said retainer piston, to move said retainermember away from said retainer anvil and release the stock toaccommodate precise positioning of stock in a machine by positioningmeans in the machine during a portion of a machine cycle, said retainerrelease cam being operable once during a portion of a machine cycle tothereby permit positioning means to precisely position the stock, andsaid retainer release means including adjustable release timing meansincorporating a gear wheel having a channel therein receiving thetransverse arms of the T-bar and establishing an index position thereof,said gear wheel being connected through a worm to a release timingadjustment knob manually operable whereby the index of the release camfollower T-bar with respect to the machine drive means is easilyadjustable to properly time the release of said retainer member with theaction of the positioning means.

10. Machine feed stock retainer apparatus comprising:

(1) a retainer anvil and retainer member spaced apart to accommodatefeed stock therebetween;

(2) a fluid operated retainer clamping piston connected to said retainermember;

(3) a retainer control valve connected to said retainer claimping pistonand to a pressurized fluid chamber;

(4) a main drive member having means thereon connectable to a machinedisposed to receive feed stock from said retainer member for operationin sychronism with the machine;

(5) positive drive means connecting said retainer control valve to saidmain drive member whereby said main drive member is operable to drivesaid retainer control valve through a sequence of valve events to movesaid retainer member to clamp the stock during a predetermined periodwith respect to operation of a machine to which the stock is fed, andtend to keep said stock clamped during said predetermined period;

(6) and retainer release means including a release cam driven by saidpositive drive means, a cam follower connected to said retainer memberand operable by said retainer release member and operaoperable by saidretainer release cam in opposition to the force applicable to saidretainer member by said retainer clamping piston, to move said retainermember away from said retainer anvil and release the stock during apredetermined portion of said period to permit location of stock in themachine independent of said retainer member.

11. The retainer apparatus as set forth in claim 10 wherein:

(1) said control valve is a rotary valve disposed under said retainerclamping piston;

(2) said cam follower includes a shaft extending centrally through saidcontrol valve and connected to said piston and having a transverse armat a lower end therof with a follower roller mounted thereon andengageable by said release cam.

12. In apparatus intermittently feeding stock to a machine, a misfeeddetector comprising:

(1) a reciprocable member having stock feeding clamp means thereon;

(2) a stock engaging detector member biased toward engagement with feedstock clamped by said clamping means, said detector member being mountedto said reciprocable member for movement simultaneously andequidistantly therewith upon absence of relative movement between thegripped stock and the reciprocavle member, said detector member beingmounted to said reciprocable member for relative movement with respectthereto upon relative movement between the gripped stock and thereciprocable member when said stock is engaged by said detector member;

(3) machine control means including a portion operatively associatedwith said stock engaging detector member and operable upon relativemovement between said detector member and said reciprocable membercaused by relative movement between said reciprocable member and thestock when the detector member engages the stock, to activate saidcontrol means and enable termination of machine operation;

(4) and release means driven by drive means driving said reciprocablemember and connected to said detector member to release said detectormember from engagement with the stock when the stock is released by theclamping meaps to accommodate a return stroke of the reciprocable memberwithout activation of said machine control means.

13. A detector as set forth in claim 12 wherein:

(1) said detector member is a pointed plunger received in a guidecylinder pivotally mounted to said reciprocable member, the pivotal axisbeing perpendicular to the direction of reciprocation of said member,and the axis of said plunger being also perpendicular to the directionof reciprocation of said reciprocable member, and

(2) said control means portion includes electrical circuit contactorsmounted on said reciprocable member and on said cylinder and cooperableto activate said control means, the relative movement of said detectormember with respect to said reciprocable member being manifested aspivotal action of said guide cylinder operable to change therelationship of said contactors, and

(3) said release include a cam and linkage, the linkage being driven bythe cam to move said plunger away from the stock.

14. Machine feed apparatus comprising:

(1) a machine feed support bracket mountable to a machine frame;

(2) a machine feed drive member rotatable on said bracket;

(3) a reciprocable gripper slide movement on said bracket;

(4) slide drive means including a shaft eccentrically mounted to saiddrive member and connected to said slide and operable during arevolution of said drive member to reciprocate said slide from a homeposition to a point for a feed stroke and then back to home position, toprovide a machine feed cycle;

(5) a machine feed gripper mounted to said slide and including firstanvil means and gripper means spaced apart to accommodate receipt ofmachine feed stock therebetween, with the gripper means having a fluidoperated gripper clamping means connected thereto and a gripper controlvalve associated with said clamping means and with a pressurized fiuidsource to control operation of said clamping means.

15. The apparatus of claim 14 and further comprising:

valve operator means coupled to said valve and operable by said drivemember to effect movement of said gripper means toward said anvil meansand clamping of stock therebetween immediately before said feed stroke,and permit movement of said gripper means away from said anvil means andrelease of stock prior to return of said slide to said home position tocomplete a machine feed cycle.

16. The apparatus of claim 14 and further comprising:

a retainer anvil and retainer member spaced apart to accommodate feedstock therebetween;

fluid operated retainer clamping means connected to said retainermember;

and a retainer control valve associated with said retainer clampingmeans and with a pressurized fluid source to control operation of saidretainer clamping means.

17. The apparatus of claim 16 and further comprising:

first valve operator means coupled to said gripper control valve and tosaid drive member and operable by said drive means toetlect movement ofsaid gripper means toward said anvil member and clamping of stocktherebetween immediately before said feed stroke, and permit movement ofsaid gripper means away from said anvil means and release of stock priorto return of said slide to said home position to complete a machine feedcycle;

second valve operator means coupled to said retainer control valve andto said drive member and operable by said drive member to eilectclamping of stock between said retainer anvil and retainer member duringsaid movement of said gripper means away from said first anvil means anduntil a subsequent feed stroke.

18. The apparatus of claim 14 wherein:

said gripper clamping means, said gripper control valve, and saidpressurized fluid source are mounted on said reciprocal gripper slide,said pressurized fluid source including a pressurized fluid chamber.

References Cited UNITED STATES PATENTS Haller 226l62 X Danly et al 83923X Loeifel 83206 X Roberts 83923 X Norton et a1 226l62 X ANDREW R.JUHASZ, Primary Examiner.

